Electro-hydraulic brake actuating system

ABSTRACT

A brake actuating system especially useful for applying the brakes of a towed vehicle concurrently with application of braking pressure in the towing vehicle is provided which includes a variable valve means interconnected to the towed vehicle&#39;s conventional type hydraulic brakes. The variable valve means controls the pressure applied to the brakes of the towed vehicle in response to variable electric current which is supplied via a variable current source which is interconnected to the brakes of the towing vehicle. Also provided, is a breakaway safety device which upon physical separation of the towed vehicle from the towing vehicle causes hydraulic pressure to be supplied automatically to the hydraulic brakes of the towed vehicle.

This invention relates to a brake actuating system wherein variedelectric current is translated first to mechanical action via anelectromagnet which controls the position of a valve stem within avariable valve means, and, secondly, to hydraulic pressure as saidvariable valve means restricts the flow of hydraulic fluid therethrough.In another aspect, this invention relates to a brake actuating systemfor use in conjunction with a towing vehicle-towed vehicle combination,whereby increased braking pressure in the towing vehicle is communicatedto the brake actuating system of the towed vehicle via increasingelectric current which by means of a unique electromagnetic variablevalve means is translated to increased hydraulic pressure delivered tohydraulic brakes of the towed vehicle. In still another aspect, thepresent invention relates to an electromagnetic variable valve meanswhich, in response to increasing electric current, causes an increase inpressure to the brakes of a towed vehicle. A further aspect of thepresent invention relates to a unique breakaway device, which, uponphysical separation of the towing vehicle from the towed vehiclesupplies instantaneous hydraulic pressure to the hydraulic brakes of thetowed vehicle.

BACKGROUND OF THE INVENTION

Until recently braking systems employed in connection with towedvehicles such as horse trailers, for example, were usually one of threeconventional types of systems. These include: electric braking systems,surge hydraulic braking systems, and vacuum over hydraulic brakingsystems. The electric type braking system conventionally includeselectromagnets mounted inside the brake drum of each wheel of the towedvehicle, which upon application of electric current attach themselves toan armature plate mounted inside the brake drum. The rotating motion ofthe wheel then carries the attached electromagnet with it causing anarmature attached to the electromagnet to rotate and expand brakingbands against the brake drum. Electric current to the electromagnet issupplied via a rheostat activated by hydraulic pressure from the brakesof the towing vehicle or by a hand control mounted in the passengercompartment of the towing vehicle. The disadvantages of such a systeminclude the fact that during normal operation, braking pressure issupplied first to the hydraulic brakes of the towing vehicle and then,as the electric brakes of the towed vehicle are activated, a noticeablelurch occurs which may affect the control of the operator of the towingvehicle during braking. Further, variance in electromagnetic strengthamong the electromagnets in each wheel may cause uneven braking andfurther control problems. Such a system is also prone to electricalwiring problems because electrical wires carrying current to eachelectromagnet are exposed between the wheel and the frame of the towedvehicle. Finally, while such electrical braking systems are sometimessupplied with an emergency breakaway kit, which includes anonrechargeable dry cell battery which automatically completes thecircuit to the electromagnet upon physical separation of the towed andtowing vehicles, these emergency breakaway systems are completelydependent on the performance of such dry cell batteries which may, overa period of time, lose sufficient charge to properly activate theelectric brakes.

A second type of conventional braking system used in conjunction withtowed vehicles are surge hydraulic brakes. These types of systemsconventionally include a piston and cylinder mounted between the towedvehicle and the towing vehicle in a manner such that when the brakes ofthe towing vehicle are applied, the momentum of the towed vehicle causesthe piston to move into the cylinder resulting in hydraulic pressurewhich is transferred to the hydraulic brake cylinders of the towedvehicle. Disadvantages of this type of system include the apparent factthat in case of brake failure in the towing vehicle, no trailer brakepressure may be applied. Further, there is no provision for handactivation of such a system, thus making this type of system illegalunder the relevant laws of some states. As is also apparent from theforegoing brief description of a conventional surge hydraulic brakingsystem, full braking power is applied to the towed vehicle when thetowing vehicle is operated in a reverse gear, whether such braking isdesired or not.

The third type of conventional braking system is the vacuum overhydraulic brake system. This type of system conventionally includes avacuum chamber, containing a diaphragm, mounted in the towed vehicle towhich vacuum is supplied from the intake manifold of the engine of thetowing vehicle. Upon activation of this type of braking systematmospheric pressure is allowed to enter one side of the vacuum chamber,thus causing the diaphragm to expand into the evacuated side of thechamber, thereby mechanically moving a rod attached to the diaphragmwhich advances a piston in the master cylinder and creates hydraulicpressure to the hydraulic brakes of the towed vehicle. Release of thebraking pressure is accomplished by reestablishment of a vacuum on bothsides of the diaphragm within the vacuum chamber. The disadvantages ofsuch a system include the necessity of leak proof vacuum lines to thevacuum source (usually the engine of the towing vehicle) and the factthat the operation of such systems is relatively slow causing a timedifference between the application of the brakes of the towing vehicleand those of the towed vehicle. As is also apparent, complete loss ofbrakes in the towing vehicle will occur in the event of engine failureor a separation or leak in the vacuum lines leading to the towedvehicle.

SUMMARY OF THE INVENTION

The electro-hydraulic brake actuating system of the present inventionovercomes the disadvantages of presently available trailer brakeactuating systems and provides for the smooth application of the brakesof a towed vehicle in response to a like application of the brakes ofthe towing vehicle. According to the invention, conventional hydraulicbrakes in the towed vehicle are actuated simultaneously with the brakesof the towing vehicle in response to increasing electric currentsupplied to a novel variable valve means which comprises a portion ofthe braking system of the present invention, the increasing electricalcurrent being supplied from the battery or other power source of thetowing vehicle, via an electric current varying means such as, forexample, a rheostat. Thus, the towed vehicle is slowed via conventionalhydraulic brakes without the necessity of any hydraulic connectionbetween the towed and towing vehicles. Further, a breakaway device isprovided which supplies hydraulic pressure to the brakes of the towedvehicle via a spring loaded piston-cylinder arrangement which isreleased upon physical separation of the towed vehicle from the towingvehicle.

Basically, the electro-hydraulic brake actuating system of the presentinvention comprises the following components. The towing vehicle issupplied with a means for varying electric current, such as a rheostat,for example, which is interconnected with the battery or otherelectrical power source of the towing vehicle. Two electrical wirescarry current from the towing vehicle to the towed vehicle, electricalconnection between the two vehicles being accomplished using any of avariety of conventional electrical connection devices. The firstelectrical wire carrying electric current to the towed vehicle isconnected to a direct current electrical motor mounted in the towedvehicle. The second electrical wire, which interconnected to the currentvarying means in the towing vehicle leads to the electromagnet of thenovel variable valve means of the present invention to be described indetail below. The direct current electric motor is used to drive amechanical hydraulic pumping means, such as a gear pump, for example.Thus, once electric current is supplied to this first electric wire, thedirect current electric motor drives the hydraulic pumping means whichin turn is interconnected hydraulically with hydraulic fluid linesleading to conventional hydraulic brake cylinders located in each wheelof the towed vehicle. The aforementioned variable valve means isinterconnected hydraulically between the outlet of said hydraulicpumping means and the inlet thereof, in a manner such that hydraulicfluid flowing out of the outlet of the hydraulic pumping means and tothe hydraulic wheel cylinders must flow through said variable valvemeans before it can return to the inlet side of the hydraulic pumpingmeans. Thus, upon application of electrical current to the directcurrent electric motor via the electrical connection between the twovehicles, the hydraulic pumping means begins to circulate fluid whichflows from the outlet of said pumping means to the hydraulic brakecylinders located in each wheel of the towed vehicle and thence throughthe variable valve means and back to the inlet of the pumping means, ora reservoir hydraulically connected to said inlet. Upon application ofelectric current to the electromagnet of the variable valve means, flowthrough said valve means is restricted incrementally in response to theamount of electric current supplied to the electromagnet. As flowthrough the variable valve means becomes so restricted, there will be aresulting increase in hydraulic pressure supplied to the wheel cylindersof the towed vehicle, because hydraulic fluid, being pumped at asubstantially constant rate by the hydraulic pumping means, will not beallowed to return to the inlet of the pumping means at the same rate atwhich said hydraulic fluid is being supplied to the hydraulic linesleading to the wheel cylinders. Thus, by supplying electric current tothe direct current electric motor at the same instant at which thebrakes of the towing vehicle are applied a slight pressure can besupplied to the hydraulic wheel cylinders of the towed vehicle, thisinitial pressure being controlled by the relationship of the pumpingrate of the hydraulic pumping means to the orifice size of the variablevalve means in its completely open position. When further brakingpressure is applied in the towing vehicle, variable electric current issupplied to the electromagnet in the variable valve means causing afurther restriction in the circulation of hydraulic fluid through thesystem, with the resulting increase in braking pressure supplied to thehydraulic wheel cylinders of the towed vehicle which is proportional tothe amount of electric current supplied to the electromagnet of thevariable valve means.

In a preferred embodiment of the present invention, a breakaway deviceis connected hydraulically to the wheel cylinders of the towed vehicle.This breakaway device, affixed to the towed vehicle, is connected to thetowing vehicle via a chain or cable so that upon separation of towedvehicle from towing vehicle, the chain or cable will mechanically pullan activating pin which will cause the breakaway device to deliverhydraulic pressure to the wheel clinders of the towed vehicle, therebybringing it to a halt. Basically, the breakaway device of the presentinvention comprises a cylinder with a spring loaded piston therein whichis normally kept in a compressed state. When the aforementionedactivating pin is pulled, because of separation of the two vehicles, thespring loaded piston within the cylinder is released and the expansionof the spring is translated into hydraulic pressure within the cylinderwhich pressure is then applied to the hydraulic wheel cylinders of thetowed vehicle.

The electromagnetic variable valve means of the present inventionbasically comprises a valve housing which has an inlet hydraulicallyconnected to the outlet of the hydraulic pumping means an an outlethydraulically connected to the inlet of the hydraulic pumping means.Mounted within the valve housing is a valve stem block having anaperture therethrough which slidably receives a valve stem therein. Thevalve stem which is slidably mounted within the aperture in the valvestem block is generally of a cylindrical shape and includes a conicalend portion which is received in a conical valve stem seat adjacent theinlet of the valve stem housing. Thus, hydraulic fluid flowing into thevariable valve means via its inlet passes through the conical valve stemseat into the valve housing and out of the inlet thereof. As the conicalend of the valve stem is moved into the valve stem seat (the valve stemand valve seat being axially aligned), the cross sectional area of thevalve stem seat through which fluid may flow decreases. If the conicalend of the valve stem is completely seated in the conical valve stemseat, substantially no fluid would be allowed to pass through the inletof the variable valve means and into the valve housing. The cylindricalvalve stem extends upward through the aperture provided therefor in thevalve stem block and the upper end of the valve stem extends for apredetermined distance out of the upper end of the aperture of the valvestem block. A plate, made of magnetic material which can, for example,be circular in shape, rests on top of the upper end of the valve stem.Electromagnetic windings are placed annularly around the valve stemblock and are connected to the aforementioned variable current source.

The operation of this electromagnetic variable valve means can bebriefly described as follows. Upon application of fluid pressure via thehydraulic pumping means, hydraulic fluid will begin to flow into theinlet of the valve housing. The pressure initially present will be suchas to lift the conical end of the valve stem out of its normally seatedposition in the valve stem seat. Thus, as fluid begins to flow into theinlet the valve stem is, in effect, floated from a seated position bythe pressure of the hydraulic fluid entering the inlet of the valve. Ifno electric current is supplied to the electromagnet of the variablevalve means, the hydraulic fluid will simply circulate through the inletof the valve housing, past the conical end of the valve stem and out theoutlet of the valve housing. However, upon application of electriccurrent to the electromagnetic windings surrounding the valve stemblock, the aforementioned plate of magnetic material resting on top ofthe upper end of the valve stem will be attracted to the electromagneticwindings and the valve stem block itself. As the plate moves downwardtoward the electromagnetic windings and the valve stem block its motionpushes the valve stem downward through the valve stem aperture in thevalve stem block causing the lower conical end of the valve stem to movetowards a seated position in the conical valve stem seat adjacent theinlet of the valve housing. In this manner, the rate of flow of fluidthrough the variable valve means may be controlled as a function of theamount of electric current supplied to the electromagnetic windings ofthe variable valve means. Increased electric current will cause themagnetic plate to move farther towards the electromagnetic windingscausing the conical end of the valve stem to move downward into thevalve stem seat thereby increasingly restricting the flow of fluidthrough the variable valve means. It is this transference of increasingelectrical current to increasing restriction of fluid flow through thevalve which allows the variable valve means of the present invention tocause increasing hydraulic pressure to be applied to the hydraulic wheelcylinders of the towed vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

A better understanding of the present invention will be facilitated by astudy of the accompanying drawings in which:

FIG. 1 is a schematic representation of the electro-hydraulic brakeactuating system of the present invention;

FIG. 2 is a sectional view of one embodiment of the novelelectromagnetic variable valve means of the present invention;

FIG. 3 is a perspective view in partial section depicting a preferredembodiment of the hydraulic pumping means, and electromagnetic variablevalve means, wherein these components are contained in a cylindricalhydraulic fluid reservoir; and

FIG. 4 is a sectional view of the novel breakaway hydraulic brakeactuator of the present invention.

DETAILED DESCRIPTION

Referring to FIG. 1 a schematic representation of one embodiment of theelectro-hydraulic brake actuating system of the present invention isdepicted. In the drawing, the conventional master cylinder 2 of a towingvehicle having conventional type hydraulic brakes is shown connectedhydraulically via hydraulic lines 4 and 6 to stop light switch 8 and anelectric current varying means 10 such as, for example, a rheostat orother variable resistor means. Stop light switch 8 is connected viaelectric wire 12 to a solenoid switch 14 which, in turn is connected viaelectric wires 16 and 18 to the battery or other power source of thetowing vehicle and a direct current electric motor located in the towedvehicle, respectively. Electric wire 20 carries the output from currentvarying means 10 to the electromagnet of variable valve means 22 locatedin the towed vehicle. Thus, electrical wires 20 and 18 are the onlyelectrical connections necessary (other than conventional types oftrailer brake light apparatus) between towing vehicle and towed vehicle.These connections may be made by any of various types of conventionalelectrical connectors, such as those used in connecting brake lightwiring between towing vehicle and towed vehicle.

Hydraulic pumping means 24 located in the towed vehicle is connectedmechanically with the direct current electric motor (not shown) which issupplied with current via electric wire 18. Hydraulic pumping means 24circulates fluid through outlet hydraulic line 26 to the hydraulic wheelcylinders of the towed vehicle schematically represented here as 28a and28b. Of course, any number of hydraulic wheel cylinders may be suppliedby hydraulic fluid from output hydraulic line 26. As shown in thedrawing, in order for hydraulic fluid to be circulated to hydraulicfluid reservoir 30 and pumped therefrom back through the hydraulic loop,the hydraulic fluid must flow through variable valve means 22.

The schematic representation of the electro-hydraulic brake actuatingsystem of the present invention depicted in FIG. 1 can be operate in thefollowing manner. When the driver of the towing vehicle applies thehydraulic brakes of the towing vehicle, the resulting pressure in mastercylinder 2 will be transmitted via hydraulic line 4 to brake lightswitch 8, which in turn will supply electric current via electrical wire12 to solenoid switch 14. Solenoid switch 14 will then move to a closedposition completing the electrical circuit between the battery of thetowing vehicle and the direct current motor in the towed vehicle, whichis mechanically interconnected with hydraulic pumping means 24. Thus,upon application of the brakes of the towing vehicle, hydraulic pumpingmeans 24 will begin to circulate fluid through outlet hydraulic line 26and to hydraulic wheel cylinders 28a and 28b. Further, hydraulicpressure in hydraulic line 6 in the towing vehicle, which will increasewith increased pressure in master cylinder 2 will cause the electriccurrent varying means 10 to supply increasing electric current viaelectric wire 20 to the variable valve means 22 in the towed vehicle.Thus, the increasing electric current, which increases in response toincreased braking pressure in the towing vehicle, will cause variablevalve means 22 to gradually close in response thereto restricting theflow of hydraulic fluid through the valve and thereby increasing thepressure in hydraulic wheel cylinders 28a and 28b. In this manner,increasing brake pressure in the towing vehicle is translated toincreasing electric current output from variable electric current means10, which in turn is translated into increasing braking pressure in thetowed vehicle as a result of the increasingly restricted hydraulic flowthrough variable valve means 22.

Thus, at the first instant of application of the brakes of the towingvehicle, hydraulic pumping means 24 begins to circulate fluid throughthe hydraulic system of the towed vehicle resulting in a slight initialpressure being exerted in hydraulic wheel cylinders 28a and 28b thusbeginning to brake the towed vehicle. The amount of initial brakingpressure caused in this manner can easily be controlled andpredetermined by adjusting the pumping rate of hydraulic pumping means24 and the orifice size of the inlet of variable valve means 22 when thevariable valve means 22 is in a full open position. For example, if noinitial braking pressure is desired, the pumping rate of hydraulicpumping means 24 can be set at a relatively low value and the orificesize of variable valve means 22 in its open position can be constructedso that there is no substantial restriction of free hydraulic flowthrough the hydraulic system of the towed vehicle. Upon further brakingaction by the driver of the towing vehicle, the electromagnet of thevariable valve means 22 (to be described in detail below) causes flowthrough the hydraulic system of the towed vehicle to be restrictedresulting in increasing braking pressure in the towed vehiclesimultaneously with the increase in braking pressure being applied inthe towing vehicle. It is noted that a hand control means for electriccurrent varying means 10 can be mounted in the passenger compartment ofthe towing vehicle, so that upon advancement of such hand control meansthe brakes of the towed vehicle can be applied without applying thebrakes of the towing vehicle. Of course, in such a case the hand controlwould also be connected electrically to solenoid switch 14, so that thedirect current electric motor, driving hydraulic pumping means 24, wouldbe activated upon use of the hand control.

Referring to FIG. 2, a preferred embodiment of an electromagneticvariable valve means useful in the present invention as variable valvemeans 22 in FIG. 1 will be described. Generally, the electromagneticvariable valve means of the present invention includes a valve having aninlet and an outlet with an electromagnetically controlled valve steminterposed between said inlet and outlet to thereby control the rate offlow of hydraulic fluid through the valve. Referring to FIG. 2, valvehousing 40 is shown in cross section and can generally be of any shapeincluding, for example, cylindrical. A valve stem block 42 is positionedwithin valve housing 40 by valve stem block locating means, such as, forexample, valve stem block locating means 44 as depicted. A valve stem 46is slidably mounted within a valve stem aperture 48 which extendsthrough valve stem block 42. Valve stem 46 is generally of a cylindricalelongated shape, the lower end 46a thereof being conical in shape. Lowerend 46a of valve stem 46 can also include a cylindrical projection 46bextending from the apex of the conical shaped lower end 46a. As shown,lower end 46a of valve stem 46 is received in a conical valve stem seat47 adjacent the inlet 41 through which hydraulic fluid enters the valve.A plate 50 of magnetic material rests on top of the upper end 52 of thevalve stem 46. In the preferred embodiment of valve stem 46 depicted inFIG. 2, the midsection of the valve stem is expanded to a largercircumference than the upper portion thereof and includes an annularsealing means 54, such as an O-ring for example. Upper end 52 of valvestem 46 can be conical in shape, as shown, and plate 50 can have aconical indentation in the center thereof to insure that the plate 50will stay in position atop valve stem 46.

Located annularly around the valve stem block 42 is electromagnet means56 which is electrically connected to the supply of variable electriccurrent 10 referred to in FIG. 1. Electromagnet means 46 can befabricated in a known manner by winding electrical wire around valvestem block 42 or any other known type of electromagnetic device can befabricated so as to fit annularly around valve stem block 42. A valvehousing top 58 can be provided to enclose the electromagnetic valvemeans as a sealed unit.

The operation of the electromagnetic valve means of this invention cangenerally be described as follows. When no hydraulic fluid is beingpumped into the valve means via valve inlet 41, the lower end 46a ofvalve stem 46 rests in a closed position in conical valve stem seat 47.Upon initiation of hydraulic pressure, hydraulic fluid will begin tocirculate into inlet 41 and cause valve stem 46 to "float" upward toallow hydraulic fluid to flow through conical valve stem seat 47 andinto the valve housing 40. If electromagnet means 56 is not activated byapplying electric current thereto, hydraulic fluid will flow into valvehousing 40 via inlet 41 through conical valve seat 47 and around lowerend 46a of valve stem 46, circulate through the valve housing, and outof the valve housing via its outlet (not shown). Upon application ofelectric current to electromagnet means 56, the electromagnetic fieldproduced thereby will begin to attract magnetic plate 50 downwardtowards valve stem block 42 and electromagnet means 56. The movement ofplate 50 in this direction will cause valve stem 46 to slide downwardwithin valve stem aperture 48 causing lower end 46a to moveprogressively towards a seated position in valve stem seat 47. Ifsufficient electric current is supplied to create a strong magneticfield the magnetic attraction will cause plate 50 to move downward untillower end 46a of valve stem 46 becomes completely seated in valve stemseat 47 adjacent the inlet. When this occurs, all hydraulic fluid flowthrough inlet 41 into the valve housing 40 will be blocked therebycreating back pressure which is transmitted via hydraulic lines to thehydraulic wheel cylinders in the brakes of the towed vehicle causingmaximum braking action to occur.

As discussed above in relation to FIG. 1, when an increasing electriccurrent is supplied to electromagnet means 56, which increases inresponse to increasing brake pressure applied in the towing vehicle,valve stem means 46 will move smoothly toward a seated position and thehydraulic brakes of the towed vehicle will thus be applied in sequencewith those of the towing vehicle. When the brakes in the towing vehicleare released, the flow of electric current to electromagnet means 56will cease, thus releasing plate 50 from magnetic attraction andallowing the pressure exerted by hydraulic fluid flowing into inlet 41to raise valve stem 46 from a seated position to an open position,thereby releasing the brakes of the towed vehicle.

It should be noted that the electromagnetic valve means of the presentinvention may be modified in a manner such that its parts are easier tomass produce departing from the concept of the present invention. Forexample, electromagnet means could be provided around a piston likeassembly slidably mounted within a cylinder, such that upon applicationof electric current to the electromagnet means, the entire pistonassembly would be attracted downward towards a magnetic surface at thebottom of the cylinder, thereby moving a valve stem means extendingthrough an aperture in the bottom of the cylinder downward to controlthe flow of fluid through the valve in a manner similar to thatdescribed above.

Referring to FIG. 3, a preferred embodiment of the present invention isshown wherein the electromagnetic variable valve means previouslydescribed is located within an enclosed hydraulic fluid reservoir which,in turn, is positioned on top of a conventional type gear pump employedas the hydraulic pumping means of the present invention. Thus, a directcurrent electric motor 60 (shown schematically) is connected via driveshaft 62 to drive gear 64 of the hydraulic pumping means. Uponapplication of direct current to electric motor 60, drive gear 64 beginsto rotate on its axis, thereby turning gear 66 and providing hydraulicpressure in the hydraulic line (not shown) leading to the wheelcylinders of the towed vehicle. A hydraulic return line, leading fromthe hydraulic brake cylinders of the towed vehicle to inlet line 41 ofthe variable valve means described above, causes fluid to flow into thevalve via conical valve seat 47 and such flow is controlled by theamount of electrical current supplied to the electromagmet means 56 asdescribed above in relation to FIG. 2. After passing through the valve,the hydraulic fluid exits therefrom via the outlet of the valve and isreturned to reservoir area 68 which can comprise a cylindricalcontainer, within which the variable valve means is mounted as shown.Thus, the novel variable valve means of the present invention, thehydraulic pumping employed therewith, and a reservoir for hydraulicfluid can be contained in a compact cylindrical unit which can easily bemounted, along with a direct current electric motor therefor, on theframe of a towed vehicle.

Referring to FIG. 4, a novel breakaway device useful in the brakeactuating system of the present invention will be described which, uponphysical separation of the towed vehicle from the towing vehicle, willautomatically supply sufficient hydraulic pressure to the wheelcylinders of the hydraulic brakes of the towed vehicle to bring it to ahalt. Generally, the breakaway device includes an elongated cylinder 70having a top plate 72 and a bottom plate 74. The top plate 72 has apiston rod aperture 74 extending therethrough which slidably receivespiston rod 76 which has a piston member 78 affixed to the lower endthereof. Bottom plate 74 includes a fluid outlet aperture 80 extendingtherethrough and a shaft 82 extending upward therefrom which includes afluid inlet aperture 84 extending therethrough. Piston rod 76 includes ashaft receiving aperture 86 therein which is axially aligned with shaft82 extending upward from bottom plate 74. A helical spring means 88(shown in a state of compression) is located between top plate 72 andpiston member 78. A locking pin 90 is mounted locking pin aperture 92which extends downward from the top of piston rod 76. Locking pin collar94 holds locking pin 90 in axial alignment with locking pin aperture 92and retains a second helical spring 96 (shown in a relaxed position)positioned around locking pin 90. As shown, the lower end of helicalspring 96 rests on an expanded portion 98 of locking pin 90 which is ofa greater diameter than the upper portion of locking pin 90 and which isconically tapered at the lower end thereof. Locking balls 100a and 100bare spherical in shape and are shown in a locked position.

Of course, piston member 78 can include conventional O-ring sealingmembers 102 and 104 to provide hydraulic seals between the piston andthe walls of elongated cylinder 72 and the piston and shaft 82. Alsoshown positioned within the hydraulic line 110 connecting the breakawaydevice hydraulically to the hydraulic pumping means is a one-way valvemeans 106 which comprises a conical valve stem seated in a conical valveseat and held in position by a spring means 108.

Operation of the breakaway device can be described in the followingmanner. When the towed vehicle is separated from the towing vehicleunintentionally, a chain or other tying means which is firmly affixed tothe towing vehicle at one end and affixed to locking pin 90 at the othercauses locking pin 90 to move upward allowing locking spheres 100a and100b to roll downward and inward out of a locking position, therebyreleasing piston rod 76 and the compressive force of helical springmeans 88. Thus, piston rod 76 and piston 78 are forced rapidly downwardwithin elongated cylinder 72 forcing hydraulic fluid, under pressure,out of outlet aperture 80 and to the hydraulic brakes of the towedvehicle via a conventional hydraulic brake line leading thereto. Ofcourse, some back pressure created by hydraulic fluid flowing out ofinlet aperture 84 extending through shaft 82 will occur until piston 78moves downward for a sufficient distance, such that shaft receivingaperture 86 mates with shaft 82, thereby sealing the fluid contained inshaft aperture 86 from the remaining fluid present in elongated cylinder72. The hydraulic pressure exerted by the spring force of helical springmeans 88, via piston 78, is sufficient to provide braking pressure tothe wheel cylinders of the towed vehicle.

One of the outstanding features of the breakaway device of the presentinvention is the ease with which the device may be reset afteractivation, so as to be ready for a second use. All the operator need dois to reconnect the electrical connections between towing vehicle andtowed vehicle and operate the towed vehicle's brakes, either bydepressing the brakes of the towing vehicle or employing a hand controltherein, so as to activate the hydraulic pumping means in the novelbraking system of the towed vehicle. The hydraulic pressure supplied bythe hydraulic pumping means will enter the breakaway device viahydraulic line 110 and inlet aperture 84 running through shaft 82,thereby exerting pressure on the upper end of shaft receiving aperture86 located within the piston rod 76. Hydraulic pressure will also beexerted on piston 78 since the braking pressure will be communicatedfrom hydraulic line 110, through one-way valve 106 and into cylinder 70via outlet aperture 80. Of course, braking pressure will also be exertedon the brakes of the towed vehicle as hydraulic fluid exerts pressure tothe brake line via hydraulic line 110 and one-way valve 106. Continuedapplication of braking pressure will cause circulation of fluid upthrough inlet aperture 84 and outlet aperture 80, exerting hydraulicpressure against the end face of shaft receiving aperture 86 and piston78. This hydraulic pressure is sufficient to move piston 78 upwards,thereby compressing helical spring means 88 and allowing the lockingmechanism to reset itself as follows. One piston rod 76 has moved upwardand spring means 88 has been compressed, locking spheres 100a and 100bwill reach their locking positions and be forced outward into lockingposition by the conical end of lower end 98 of locking pin 90, which inturn is being forced downward by helical spring means 96, which wasplaced in a compressed state upon activation of the breakaway device bythe pulling of locking pin 90 upward. Thus, locking spheres 100a and100b will roll to a locking position, so that when braking pressure isreleased, piston 78 and piston rod 76 will remain in a locked positionwith helical spring means 88 in a compressed state ready for reuse.

The breakaway device previously described is also useful as a safetycheck on the hydraulic braking system of the towed vehicle. For example,if the breakaway device is activated intentionally by pulling lockingpin 90 upward and allowing a hydraulic fluid braking pressure to beexerted on the brakes of the towed vehicle, the towed vehicle willremain in a braked state and cannot be easily moved unless the breakaway device is reset as described above. Thus, if when the towed vehicleis attached to the towing vehicle and proper electrical connections havebeen made, the hydraulic pumping means is for some reason inoperable thebreakaway device will not be reset by applying the brakes of the towingvehicle and therefore braking pressure in the towed vehicle will not bereleased. Thus, the breakaway device effectively serves as a safetycheck to insure that the hydraulic braking system of the towed vehicleis in operating condition.

While this invention has been described in relation to its preferredembodiments, it is to be understood that various modifications thereofwill now be apparent to one skilled in the art upon reading thespecification and it is intended to cover such modifications as fallwithin the scope of the appended claims.

What is claimed is:
 1. A brake actuating system for towed vehicleshaving hydraulic brakes comprising:(a) a hydraulic fluid pumping meanshaving an outlet connected hydraulically with hydraulic brakes of saidtowed vehicle; (b) reservoir means hydraulically interconnected with theinlet of said pumping means; and (c) a normally open variable valvemeans interconnected hydraulically between the inlet of said pumpingmeans and the hydraulic brakes for restricting the flow of fluid fromsaid hydraulic brakes to said reservoir as said valve closes, saidvariable valve means comprising an electromagnetically controlled valvestem means interconnected to a means for supplying variable electriccurrent to thereby incrementally regulate the flow of fluid through saidvariable valve means according to the electric current supplied to theelectromagnet.
 2. The brake actuating system of claim 1 wherein saidmeans for supplying variable electrical current comprises the electricalpower source of a towing vehicle interconnected to a means for varyingelectric current, said electric current varying means beinghydraulically connected to the master brake cylinder of the towingvehicle so as to provide increased current in response to increasingpressure in said cylinder.
 3. The brake actuating system of claim 2wherein said means for varying electric current is a rheostat.
 4. Thebrake actuating system of claim 2 wherein said hydraulic fluid pumpingmeans is electrically driven.
 5. The brake actuating system of claim 4wherein said electrically driven hydraulic fluid pumping means isactuated by switching means interconnected between said electricallydriven pumping means and the electric power source of the towingvehicle.
 6. The brake actuating system of claim 5 wherein said switchingmeans is the brake light switch of the towing vehicle.
 7. The brakeactuating system of claim 6 and further comprising a hand control meansmechanically connected to said current varying means and electricallyconnected to said switching means for regulating electric current tosaid electromagnet and supplying electric current to said electricallydriven pumping means.
 8. The brake actuating system of claim 1 andfurther comprising a spring loaded breakaway device hydraulicallyinterconnected to said hydraulic brakes so that upon physical separationof the towed vehicle from the towing vehicle a mechanical springcompressive force is released thereby imparting fluid pressure to thehydraulic brakes.
 9. The brake actuating system of claim 8 wherein saidspring loaded breakaway device is hyraulically interconnected with saidhydraulic fluid pumping means and wherein said breakaway devicecomprises a one-way valve which allows fluid to flow to the breakawaydevice from said pumping means but not in the opposite direction andfurther comprising an automatic locking means thereby once the spring ofthe spring loaded breakaway device is put in a state of compression fromhydraulic force exerted by said hydraulic pumping means it is locked insaid state and remains under compression until released by mechanicalaction.